EP3483478A1 - Roue dentée, en particulier roue intermédiaire, pour un entraînement de roue - Google Patents

Roue dentée, en particulier roue intermédiaire, pour un entraînement de roue Download PDF

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Publication number
EP3483478A1
EP3483478A1 EP18203450.4A EP18203450A EP3483478A1 EP 3483478 A1 EP3483478 A1 EP 3483478A1 EP 18203450 A EP18203450 A EP 18203450A EP 3483478 A1 EP3483478 A1 EP 3483478A1
Authority
EP
European Patent Office
Prior art keywords
wheel
gear
wheel part
drive
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP18203450.4A
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German (de)
English (en)
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EP3483478B1 (fr
Inventor
Jens Türk
Marcus Viet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Truck and Bus SE
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MAN Truck and Bus SE
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP3483478A1 publication Critical patent/EP3483478A1/fr
Application granted granted Critical
Publication of EP3483478B1 publication Critical patent/EP3483478B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F16H2055/185—Special devices for taking up backlash using compound gears with coincident teeth of different material, e.g. laminated construction of metal and elastomeric gear layers, where elastic layer is slightly oversized
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs

Definitions

  • the invention relates to a gear, in particular intermediate, for tooth backlash reduction in a gear drive.
  • Gearboxes which are subject to widely varying torques, are prone to gear rattle at low engine speeds and to gearbox whistles at high engine speeds. This phenomenon is particularly pronounced when driving air compressors on commercial vehicle engines. Piston air compressors have the property that the sign of the torque reverses briefly after the top dead center is exceeded due to re-expansion. The result is a collision of the tooth flanks and the resulting acoustic rattles.
  • the DE 100 58 482 A1 proposes a gear for the angular momentum damping before. Unwanted noise is avoided in that a gear is formed of two wheel parts, which are connected via an elastomer torque-locking. In the uninstalled state, the teeth of the wheel parts are twisted against each other. After installation of the gear wheel parts are rotated to each other so that the teeth are almost aligned. This is achieved in that the teeth of a meshing with the gear further gear hold the teeth of the wheel parts in this position. As a result of the rotation and the restoring moment resulting therefrom, a permanent prestress is generated by the elastomer, so that the tooth flanks of the wheel parts and of the gear meshing therewith are always in positive contact.
  • the invention is based on the object to provide an alternative or improved gear for a gear drive, which, in particular when used as an intermediate wheel, enables effective backlash reduction or compensation.
  • an intermediate hereby the possibility to be created, the backlash on a driving wheel and a driven wheel via the intermediate wheel to reduce or compensate.
  • the gear may in particular be an intermediate.
  • the gear is suitable for backlash reduction and / or backlash compensation in a wheel drive.
  • the gear has a first wheel part with a plurality of teeth, which are distributed over a circumference of the first wheel part on.
  • the first wheel part is rotatable about a first axis.
  • the gear has a second wheel part with a plurality of teeth, which are distributed over a circumference of the second wheel part on.
  • the second wheel part is rotatable about a second axis parallel to the first axis.
  • the parallel arrangement of the first axis and the second axis causes the second wheel part is mounted eccentrically to the first wheel part.
  • the center of rotation of the first wheel part and the center of rotation of the second wheel part are offset in the installed state in a radial direction by the distance of the first axis to the second axis.
  • a displacement in the circumferential direction can be generated between the plural teeth of the first wheel part and the plural teeth of the second wheel part (the teeth are not aligned with each other).
  • the gear can be used as an intermediate in a gear drive for backlash reduction or compensation, the Zahnlastflanken Touch is taken into account by the drive wheel on the intermediate and from the intermediate to the output.
  • the tooth flanks of the teeth of the first wheel part are brought into contact with the load flanks of a drive wheel and a driven wheel of the gear drive for transmitting a torque from the drive wheel via the intermediate gear to the output gear.
  • the eccentric mounting of the second wheel part allows the teeth of the second wheel part and the first wheel part to be offset relative to one another in such a way that the tooth flanks of the second wheel part engage with the rear flanks of the drive wheel and the driven wheel.
  • the teeth of the first wheel part can be distributed uniformly over an outer circumference of the first wheel part.
  • the teeth of the second wheel part can be distributed uniformly over an outer circumference of the second wheel part.
  • a number of the plurality of teeth of the first wheel portion may correspond to a number of the plurality of teeth of the second wheel portion.
  • the plurality of teeth of the first wheel part and the plurality of teeth of the second wheel part may be constructed the same.
  • the second wheel part is elastically deformable in regions in a radial direction with respect to the second axis.
  • the second wheel part can be made in regions of an elastic material, having an elastic element and / or an elastic structure.
  • the elasticity of the second wheel part in combination with the eccentric position of the center of rotation of the second wheel part, allows its tension between the rear flanks of the drive wheel, the trailing edges of the driven wheel and the bearing of the second wheel part.
  • the second wheel part can deform elastically in order to adapt to the resulting from the manufacturing tolerances layers of the rear edges of input and output.
  • the second part of the wheel should not deform elastically at a change of sign of the drive torque or output torque.
  • the goal is to prevent lifting of the load flanks. This is achieved by the biasing force from the eccentric seat of the center of rotation of the second wheel part and its elasticity compensates for the negative portion of the torque and it comes at this moment to no elastic deformation of the second wheel part and the lifting of the load flanks.
  • the elasticity of the second wheel part has a positive effect on the adaptation to the manufacturing tolerances and the resulting in practice backlash. Alternatively, this could also be ensured by screwing the first and the second bearing pin.
  • the second wheel part is rotatable relative to the first wheel part.
  • the first wheel part may be solid.
  • the second wheel part has at least one gear plate.
  • the at least one gear plate is elastically deformable in a radial direction with respect to the second axis.
  • the use of gear plates for example, having a material thickness of about 1 mm, allows the integration of the elasticity in the structure of the gear plates, for example by providing slots in the gear plates.
  • a plurality of gear plates are provided, which are arranged side by side and / or form a gear plate package.
  • the gear plates may be aligned in alignment with each other in an axial direction.
  • the second wheel part and / or the at least one gear plate is made of a spring steel.
  • the at least one gear plate for providing an elasticity of the second wheel part at least one elongated hole, preferably a plurality of slots, on.
  • the at least one slot extends in a circumferential direction about the second axis, in particular circular and / or spiral.
  • the gear has a first wheel bolt about which the first wheel part is rotatably mounted.
  • the gear wheel has a second wheel bolt about which the second wheel part is rotatably mounted.
  • the first wheel bolt and the second wheel bolt can be attached to each other eccentrically to each other, in particular via a press fit.
  • the gear has a first plain bearing bush, which is arranged between the first wheel bolt and the first wheel part, on.
  • the gear on a second plain bearing bush which is arranged between the second wheel bolt and the second wheel part on.
  • a particular central lubrication channel may be provided in the first wheel bolt and / or the second wheel bolt.
  • a first radial channel may extend from the lubrication channel to the first plain bearing bush and / or a second radial channel may extend to the second plain bearing bush for supplying a lubricating fluid.
  • a lubricating fluid may be supplied to the lubrication channel via passages in a crankcase of the internal combustion engine.
  • the first radial channel and / or the second radial channel may be provided in the first wheel bolt, between the first wheel bolt and the second wheel bolt or in the second wheel bolt.
  • the toothed wheel may have at least one further wheel part, which may be formed in each case corresponding to the second wheel part of the intermediate wheel.
  • a separate "second" wheel part can be provided for each output gear.
  • the invention also relates to a wheel drive for a motor vehicle.
  • the gear drive has an idler gear that is a gear as disclosed herein.
  • the gear drive has a drive wheel, which meshes with the first wheel part of the intermediate gear and the second wheel part of the intermediate gear.
  • the gear drive has a driven wheel, which meshes with the first wheel part of the intermediate gear and the second wheel part of the intermediate gear.
  • the gear drive can achieve the advantages described herein for the gear.
  • load flanks of the drive wheel and load flanks of the output gear are in engagement with the first wheel part.
  • rear flanks of the drive wheel and rear flanks of the driven gear are in engagement with the second wheel part.
  • the second axis is offset with respect to the first axis in a direction of an angle bisector with respect to an angle defined between a rotational axis of the drive wheel, the first axis and an axis of rotation of the output gear.
  • This staggered arrangement allows the tooth flanks of the second wheel part to be brought into abutment with the trailing edges of both the drive wheel and the driven wheel.
  • the plurality of teeth of the first wheel member contact load flanks of the drive gear and load flanks of the output gear.
  • the plurality of teeth of the second wheel member contact rear edges of the drive gear and trailing edges of the output gear.
  • the load flanks and the trailing edges of the drive gear may be opposite.
  • the load flanks and the trailing edges of the output gear may face each other.
  • a tension of the second wheel part which results in particular from the staggered arrangement between the first wheel part and the second wheel part and an elasticity of the second wheel part, a lifting of the plurality of teeth of the first wheel part of load flanks of the drive wheel and load flanks of Abtriebsrads counteracts a sign change of the drive torque and / or the output torque and / or torsional vibrations.
  • a plurality of driven wheels are provided, which mesh with the intermediate gear.
  • a further wheel part of the intermediate gear is provided which is formed in each case corresponding to the second wheel part of the intermediate gear.
  • the invention also relates to a motor vehicle, in particular a commercial vehicle (for example a truck or a bus).
  • the motor vehicle has a gear drive as disclosed herein.
  • the motor vehicle has a compressor for compressing air, which is driven via the gear drive.
  • gear as disclosed herein and / or the gear drive disclosed herein may also be used to reduce and / or prevent transmission of torsional vibrations of a crankshaft of an internal combustion engine.
  • FIGS. 1 to 3 a schematic model of a wheel drive 10 according to the present disclosure is shown in various views for explaining the operation of the wheel drive 10.
  • the gear drive 10 has a drive wheel 12, an intermediate 14 and driven gear 16.
  • the drive wheel 12 meshes with the intermediate gear 14, which in turn meshes with the output gear 16. It is also possible that a plurality of driven wheels 16 mesh with the intermediate gear 14.
  • the drive wheel 12, the intermediate 14 and the output 16 are each rotatably mounted on corresponding wheel bolts.
  • the wheel bolts of the gears 12, 14 and 16 are for example via screws 34 (see FIG. 2 ) attached to the crankcase of the internal combustion engine.
  • the drive wheel 12 is rotatably mounted on a wheel bolt 18 (see FIG. 2 ) stored.
  • the drive wheel 12 may, for example, by a crankshaft 20 (schematically in FIG FIG. 2 shown) of an internal combustion engine of a motor vehicle are driven.
  • the motor vehicle may be, for example, a commercial vehicle, in particular a bus or a lorry. It is also possible that the drive wheel 12 is otherwise driven.
  • the output gear 16 is rotatably mounted on a wheel bolt 22 (see FIG. 2 ) stored.
  • the output gear 16 may, for example, for driving a secondary consumer 24 (schematically in FIG FIG. 2 shown) of the motor vehicle.
  • the secondary consumer 24 due to its operation and / or configuration tend to rotational irregularities and torsional vibrations in the form of a torque curve with sign change.
  • the auxiliary consumer 24 may be, for example, an oil pump, a hydraulic pump or an air compressor.
  • the air compressor also called Heilerpresser
  • the air compressor can, for example, operate on the principle of a plunger compressor. Air is drawn in through an intake valve of the air compressor, compressed in a cylinder of the air compressor by a piston of the air compressor and pushed out via an exhaust valve of the air compressor. Due to the design remains a residue of compressed air after pushing out in the cylinder. This residual air expands after exceeding the top dead center of a piston movement of the piston and returns energy via a drive kinematics of the air compressor.
  • the present disclosure at least compensates for or reduces the backlash between the drive wheel 12 and the idler gear 14 and between the idler gear 14 and the output gear 16 such that increased wear and noise is prevented or at least reduced.
  • the intermediate gear 14 has a first wheel part 26 and a second wheel part 28.
  • the first wheel part 26 is rotatable about a first axis A (see FIG FIG. 2 ) stored.
  • the second wheel part 28 is rotatable about a second axis B (see FIG FIG. 2 ), which is offset and arranged parallel to the first axis A.
  • the second axis B of the second wheel part 28 is arranged offset in a radial direction of the first axis A of the first wheel part 26 to the first axis A.
  • the second wheel part 28 is displaced along an arrow C.
  • the arrow C extends along an angle bisector.
  • the bisector halves an angle which is defined between a rotational axis of the drive wheel 12, the first axis A and a rotational axis of the driven gear 16.
  • the bisecting line runs through the first axis A.
  • the second wheel part 28 is arranged so offset from the first wheel part 26, the tooth flanks of the second wheel part 28 rear edges of the drive wheel 12 and the output gear 16 contact.
  • the center of rotation of the first wheel part 26 (axis A) and the center of rotation of the second wheel part 28 (axis B) are offset in the installed state in a radial direction by the distance of the first axis A to the second axis B. Thereby, an offset in the circumferential direction is generated between the plurality of teeth 36 of the first wheel member 26 and the plurality of teeth 42 of the second wheel member 28.
  • the first wheel part 26 is rotatably mounted in particular about a first wheel bolt 30 of the intermediate gear 14.
  • the first wheel bolt 30 has the first axis A as a central axis.
  • the position of the first axis A and thus of the first wheel part 26 depends on the operating gear of the classic gear design between the drive wheel 12, the intermediate gear 14 and the output gear 16.
  • the second wheel part 28 is rotatably mounted in particular about a second wheel bolt 32.
  • the second wheel bolt 32 has the second axis B as a central axis.
  • the first wheel part 26 is rotatable relative to the second wheel part 28.
  • the first wheel bolt 30 and the second wheel bolt 32 may be fastened to each other by means of screws 34. However, it is, for example, an interference fit between the wheel bolts 30, 32 possible.
  • the screws 34 may fasten the wheel bolts 18, 22, 30 and 32, for example, to a crankcase of the internal combustion engine.
  • the first wheel part 26 has, on an outer circumference thereof, a plurality of teeth 36 uniformly distributed over the outer periphery.
  • the teeth 36 mesh with teeth 38 of the drive wheel 12 and with teeth 40 of the output gear 16.
  • the drive wheel rotates 12, for example, counterclockwise in a rotational direction D (see FIGS. 2 and 3 ).
  • the drive wheel 12 drives the intermediate gear 14.
  • the intermediate 14 rotates clockwise.
  • load flanks 38A of the teeth 38 of the drive wheel 12 mesh with first load flanks 36A of the teeth 36 of the first wheel part 26 of the intermediate gear 14.
  • the intermediate wheel 14 in turn drives the output gear 16.
  • the output gear 16 rotates counterclockwise.
  • second load flanks 36B which lie opposite the first load flanks 36A, of the first wheel part 26 of the intermediate gear 14 mesh with load flanks 40A of the output gear 16. Due to the assembly and thus the gears 12, 14 can run freely, there is between the trailing edges 38B of the drive wheel 12, which are the load flanks 38A opposite, and the second load flanks 36B of the first wheel part 26 of the intermediate 14, a backlash. Likewise, there is due to the assembly and thus the gears 14, 16 can run freely, between trailing edges 40B of the driven gear 16, which lie opposite the load flanks 40A, and the first load flanks 36A of the first wheel part 26 of the intermediate 14 a backlash. This backlash can be compensated by the second wheel part 28 of the intermediate 14 or at least significantly reduced.
  • the second wheel part 28 has, on an outer periphery thereof, a plurality of teeth 42 uniformly distributed over the outer periphery.
  • the second wheel part 28 is clamped between the drive wheel 12, the output gear 16 and the second wheel bolt 32, the first tooth flanks 42 A of the teeth 42 of the second wheel part 28 of the intermediate 14 mesh with the trailing edges 38 B of the teeth 38 of the drive wheel 12.
  • second tooth flanks 42B of the teeth 42 of the second wheel part 28 of the intermediate gear 14 mesh with the trailing edges 40B of the teeth 40 of the output gear 16.
  • the second wheel part 28 has an elastic region 44.
  • the elastic region 44 can be formed, for example, by oblong holes which, for example, extend helically around the second axis B.
  • the second wheel part 28 may be made of a spring steel, for example. Due to the elastic region 44, the second wheel part 28 is elastically deformable in a radial direction toward the second axis B.
  • the rotation center of the second wheel part 28 is arranged eccentrically to the rotation center of the first wheel part 26.
  • the second wheel part 28 is partially elastically deformable.
  • the biasing force generated by the eccentricity and the elasticity of the second wheel part 28 between the second wheel part 28 on the one hand and the drive wheel 12 and output gear 16 on the other hand prevents the lifting of the load flanks of the gears 12, 14 and 16. This can prevent the formation of unwanted acoustic emissions and increased wear on the tooth flanks are avoided.
  • the intermediate gear 14 can compensate for the effects of the backlash on the drive wheel 12 and the output gear 16 by the eccentrically offset second wheel member 28 with a corresponding design.
  • the biasing force is ensured by the elasticity of the second wheel member 28 and the eccentric offset of the center of rotation of the second wheel member 28 relative to the first wheel member 26 and is necessary to avoid lifting on the load flanks.
  • the magnitude of the tension of the second wheel part 28 can be realized and adjusted by the eccentricity and / or the elasticity of the second wheel part 28.
  • the dimensioning of these parameters takes place as a function of the size of the backlash between the meshing wheels 12; 14 and 16 and the negative parts of the torque to be transmitted.
  • the eccentricity of the center of rotation of the second wheel member 28 with respect to the center of rotation of the first wheel member 26 is necessary so that the tooth flanks 42A of the second wheel member 28 on the trailing edges 38B of the drive wheel 12 abut and at the same time bear the tooth flanks 42 B of the second wheel part 28 on the trailing edges 40 B of the output gear 16.
  • This function would not be feasible with a second wheel part mounted concentrically with the first wheel part.
  • the intermediate gear 14 has the first wheel part 26 and the second wheel part 28.
  • the first wheel part 26 is rotatably mounted on the first wheel bolt 30 via a first plain bearing bush 46.
  • the second wheel part 28 is mounted rotatably on the second wheel bolt 32 via a second plain bearing bush 48.
  • the first wheel part 26 and the second wheel part 28 are rotatable relative to each other.
  • the offset of the teeth 36 of the first wheel member 26 and the teeth 42 of the second wheel member 28 and the eccentric arrangement of the center of rotation of the second wheel member 28 with respect to the center of rotation of the first wheel member 26 are in typical application examples, as in the FIGS. 4 to 6 shown embodiment, barely visible.
  • the first wheel part 26 is solid.
  • the second wheel part 28 is formed from a package of a plurality of (eight in the embodiment) juxtaposed gear plates 50.
  • the gear plates 50 may for example have a material thickness of 1 mm.
  • the gear plates 50 are aligned in an axial direction in alignment with each other.
  • the gear plates 50 are elastically deformable in a radial direction with respect to a rotation axis of the second wheel part 28. To provide the elasticity of the gear plates 50, these have a plurality of slots 44.
  • the elongated holes 44 extend in a circular or spiral manner in a circumferential direction about the rotation axis of the second wheel part 28.
  • the gear plates 50 may be made of a spring steel.
  • the idler 14 additionally has a thrust washer 52.
  • the wheel bolts 30, 32 can be fastened via a plurality of screws (not shown) to a crankcase of the internal combustion engine.
  • the wheel bolts 30, 32 may be secured to each other via a press fit.
  • the thrust washer 52 can sit with a press fit on the second wheel bolt 32. Thereby, the intermediate gear 14 can be mounted as a unit.
  • the thrust washer 52 axially supports the gear plates 50, thereby preventing the gear plates 50 from bending.
  • the plain bearing bushes 46, 48 may be formed as a hydrodynamic sliding bearing, which must be supplied with sufficient lubricating fluid during operation.
  • the lubricating fluid may be supplied from a central lubricating fluid passage 54 in the first and second wheel bolts 30, 32 via radial passages in the wheel bolts 30, 32 to the plain bearing bushes 46, 48.
  • the invention is not limited to the preferred embodiments described above. Rather, a variety of variants and modifications is possible, which also make use of the inventive idea and therefore fall within the scope.
  • the invention also claims protection of the subject matter and the features of the subclaims independently of the claims referred to.
  • the features of the subclaims are also disclosed independently of all the features of independent claim 1 and, for example, independently of the features relating to the presence and the configuration of the first wheel part and / or the second wheel part of independent claim 1.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
EP18203450.4A 2017-11-09 2018-10-30 Entraînement de roue Active EP3483478B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017126205.9A DE102017126205A1 (de) 2017-11-09 2017-11-09 Zahnrad, insbesondere Zwischenrad, für einen Rädertrieb

Publications (2)

Publication Number Publication Date
EP3483478A1 true EP3483478A1 (fr) 2019-05-15
EP3483478B1 EP3483478B1 (fr) 2020-09-16

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EP18203450.4A Active EP3483478B1 (fr) 2017-11-09 2018-10-30 Entraînement de roue

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US (1) US11320035B2 (fr)
EP (1) EP3483478B1 (fr)
BR (1) BR102018072999B1 (fr)
DE (1) DE102017126205A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102020006332A1 (de) 2020-10-15 2022-04-21 Bernhard Brehm Spielfreie Verzahnung
DE102022126015B3 (de) 2022-10-07 2024-02-15 Bcs Automotive Interface Solutions Gmbh Zahnradanordnung für einen Sensor sowie Lenkwinkelsensor-Baugruppe

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EP3483478B1 (fr) 2020-09-16
BR102018072999A2 (pt) 2019-10-01
US11320035B2 (en) 2022-05-03
US20190136955A1 (en) 2019-05-09
BR102018072999B1 (pt) 2023-10-03
CN109882568A (zh) 2019-06-14
DE102017126205A1 (de) 2019-05-09
RU2018139318A3 (fr) 2022-04-29

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